Automatic pattern controlled milling machine



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AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed June 10, 1943 7 Sheets-Sheet 4 Dec. 10, 1946. E. w. YATES ET AL 2,412,549

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Dec. 10, 1946. E. w. YATES EI'AL 2,412,549

AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed June 10, 1945 7 Sheets-Sheet 7 1NVENTOR5 fow/woM )Zm-zs Patented Dec. 10, 1946 AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Edward W. Yates and Taft S. Armandrofi, Cincinnati, Ohio, assignors to The Cincinnati Milling Machine 00., tion of Ohio Cincinnati, Ohio, a corpora- Application June 10, 1943, Serial No. 490,366

Claims.

This invention relates to milling machines and more particularly to automatic pattern controlled milling machines.

In the formation of irregular surfaces on a work piece by automatic means, it is common practice to utilize a pattern for engagement by a tracer, which is usually connected to the tool support to govern or control the irregular path of movement of the tool.

Some operations of this kind are rather simple in that they are merely an outlining operation, requiring two-directional movement, while others are more complicated, ultimately requiring threedirectional movement of the cutting tool in order to complete the operation. In many cases it is necessary to combine the different methods of operation, such as forming one portion of a surface by pattern controlling two-directional movement of the tool in one plane, and then changing over and pattern controlling two-directional movement of the tool in a second plane usually at right angles to the first plane. When' the work has a constant cross-sectional shape in a given direction it becomes possible to utilize a relatively thin two-dimensional plate as a pattern rather than a large three-dimensional block.

In view of all of these various requirements and methods of operation it is an object of this invention to provide a pattern controlled milling machine having a cutting tool which is capable of three-directional relative movement with respect to a work piece, that is, axially and two directions laterally, with improved control means whereby in a single machine it is easily and readily possible to selectively pattern control the axial movement only; pattern control the two lateral movements simultaneously and in variable proportion whereby a 360 orbit may be obtained; or to control simultaneously all three directions of movement of the tool and in an automatic manner.

Another object of this invention is to provide an automatic three-directional pattern controlled milling machine.

A further object of this invention is to provide a pattern controlled milling machine with two automatic pattern controlled tracers and suitable selective connections whereby either may be used individually to automatically control movement of the tool in respective planes. or intercoupled for simultaneously controlling the movement of the tool in three directions simultaneously.

An additional object of this invention is to provide a dual tracer, pattern controlled milling machine with means for individually adjusting the tracers relative to one another and with respect to the cutting tool for set-up purposes and to provide means for preventing movements dictated by one tracer from being imparted to the other tracer whereby simplified patterns may be used to produce a three-dimensional surface on the work.

the bed integral with the column, and a piston Other objects and advantages of the present invention should be readily apparent by reference to the following specification, considered in conjunction with the accompanying drawings forming a part thereof and it is to be understood that any modifications may be made in the exact structural details there shown and described, within the scope of the appended claims, without departing from or exceeding the spirit of the invention.

Referring to the drawings in which like reference numerals indicate like or similar parts:

Figure 1 is an elevation of a machine tool embodying the principles of this invention.

Figure 2 is an end elevation of the machine shown in Figure 1 as viewed from the right hand side of that figure.

Figure 3 is an enlarged view of the depth control tracer bracket including a cross sectional view through the tracer mechanism.

Figure 4 is an enlarged view of the other tracer support including a section through the tracer control valve.

Figure 5 is a section on the line 5-5 of Figure 2.

Figure 6 is a section on the line 6--6 of Figure 3.

Figure '7 is a section on the line '|l of Figure 3.

Figure 8 is a detailed section on the line 8-8 of Figure '7.

Figure 9 is a detailed view of the pattern support adjusting mechanism.

Figure 10 is a detail section on the line Ill-40 of Figure 5.

Figure 11 is a diagrammatic view of the hydraulic control circuit.

Figure 12 is a section on the line l2--l2 of Figure 2.

Referring to the drawings and more particularly to Figures 1 and 2 the reference numeral l0 indicates the bed of the machine upon which a table H is slidably mounted and adapted to be propelled by a piston I 2 slidably mounted in a cylinder [3, and connected by a piston rod M to the table. A column l5 uprises at the rear of to which it is integrally connected. The column has vertical guideways [6 formed thereon upon which slides a vertically movable carrier l1. This carrier is adapted to be propelled by a piston I8 contained in a cylinder IS, the cylinder being rod 20 serves to connect the piston to the slide. On account of the weight of the slide l1, and the other parts attached thereto which are to be described, the slide I1 is counterbalanced by a counterweight 2| which is connected to the slide by a chain 22 passing over pulleys 2'3 and 24 mounted in a bracket 25 attached to the top of the column.

The slide H has horizontal guideways 26 formed therein for slidably supporting a spindle (i0 carrier 21 for movement toward and from the however, in Figures 2 and 11 table. The spindle carrier is also adapted to be propelled by a hydraulic motor comprising a cylinder 28 containing a piston 29 which is operatively connected by a piston rod 30 to the carrier 21. The cylinder 28 is fixed in the slide I1.

Power feeding and manual adjustment of the three slides is controlled by individual servovalves. As shown in Figurell, the piston and cylinder motor I2, |3 for the table is adapted to be controlled by a servo-valve indicated generally by the reference numeral 3| which has a pressure port 32, a. pair of exhaust ports 33 and 34, and a pair of motor ports 35 and 36. The channels 31 and 38 from ports 35 and 36 terminate in ports 39 and 40 of a selector valve having a plunger,

When the plunger is in the position shown in Figure ll the ports 39 and 40 are connected to ports 42 and 43respectively which have channels 44 and 45 that terminate in opposite ends of the cylinder I3. When the servo-valve plunger 46 is in a central position as shown, the piston I2 and thereby the table is held stationary. The is adapted to :be moved by a servo-screw The piston and cylinder I8, I9 for the vertical slide I1 have a servo-valve indicated generally by the reference numeral 48 which has a pressure port 49. a pair of exhaust ports 50 and and a pair of motor ports 52 and 53. These latter ports are connected by channels 54 and 55 to ports 56 and 51 of a selector valve having a control plunger 58. When this plunger is in the position shown, the ports 56 and 51 are connected to ports 59 and 60 from which channels 6| and 62 extend to opposite ends of the cylinder I9. servo-valve plunger 63 is in the position shown all flow to and from the cylinder I9 is cut oil and the piston I8 is held stationary. The valve plunger 63 may be operated by a servo-screw 64-.

The piston and cylinder motor 29, 28 for the spindle carrier slide 21 has a servo-valve indicated generally by the reference numeral 65 in which is a pressure port I56,v a pair of exhaust ports 61 and 68 and a pair of motor ports 69 and 10. These latter ports are connected by channels 1| and 12 to a selector valve indicated generally by the reference numeral 13 and having a plunger 14 in which is formed grooves 15 and 16 for interconnecting channels 1| and 12 to channels 11 and 18 which terminate in opposite ends of the cylinder 28. When the servo-valve plunger 19 is in the central position shown, the piston 29 is held stationary. The valve'plunger 19 may be actuated by a servo-screw 80.

The various servo-valve control screws 41, 64 and 80 may be power actuated ormanually actuated by a mechanism such as that shown in U. S. Patent No. 2,239,625, issued April not believed to be necessary. The various hand wheels for rotating the servo-screws are shown, and in these figures the hand wheel 8| is Operatively connected to the servo-screw 41, the hand wheel 62 is operatively connected to the servo-screw 80 and the hand wheel 83 is operatively connected to the servoscrew 64.

hNo power means have been provided in this ma- 0 in f means will be" immobilized, At the same time the servo-screws must be operatively disconnected from the actuated slide. This is all accomplished automatically by admitting pressure to one channel which is the channel 84 shown in Figure 11 having one terminus connected to port 85 of the selector valve 86 which contains the plunger 4|. This valve has a pressure port 88 which is connected by the plunger 4|, when it is shifted to the right of the position shown, to port 85 whereby pressure is admitted to channel 84.

This channel has a first branch line 89 terminating in a pair of cylinders 90 which contain plungers for rotating the power transmission not shown for the vertical servo-screw 64, but which is connected to the gear 81. A second branch connection 93 serves to connect channel 84 to a pair of cylinders 94 containing plungers, for rotating a lever 95 centrally connected to a shaft 96 for disconnectin the power transmission to the servoscrew 41.

A third branch connection connects this channel to a disengageable nut 98 for disconnecting the servo-valve plunger 46 from the table servoscrew 41. Another branch channel 99 terminates in a cylinder I00 having a plunger I 0| for camming the nut portions I02 out of engagement with the screw 64 whereby the vertical slide I1 may move independent of the screw. I

For automatic tracer controlled operations the vertical slide and the tabl are operatively connected for control by a tracer control valve indicated generally by'the reference numeral I03 which supports a tracer finger I04 and shown in Figures 2 and 4. The cross slide or spindle carrier 21 is operatively connected to a tracer control valve I05 which, in turn, is controlled by a tracer finger I06 as shown in Figure 3. It will be noted that the selector valve plungers 58 and 4| in Figure 11 are operatively connected to a rotatable crank I01 fixed on a rotatable shaft I08 for joint operation.

The two plungers 5B and 4| together constitute a selector valve which selectsbetween manual operation and automatic tracer controlled operation of the. table II and the vertical slide I1. The plungers are shown in a manual control position and are held in this position by a spring pressed latch I09. When this latch is removed a spring 0 operating on the end of plunger 58 shifts it to the left, as viewed in Figure 11, and through crank I01 shifts the plunger 4| to the right. This results in the following connections being established.

The ports 59 and 60 which control the piston I8 are connected by the annular grooves III and 2 to ports 3 and 4 which have channels I 5 The valve II9 has a pair of pressure ports I29 and I30 and the valve I28 has a pair of pressure ports |3| and I32 and all of these pressure ports are connected to a common supply channel I33 which is connected to port I34 of a, feed-rapid traverse selector valve I35. This valve is supplied by a rapid traverse pump I 36 and a feed pump I31 which have suitable intakes for withdrawing fluid from a reservoir I38 and individual channels I39 and I40 which terminate at ports MI and I42 in the selector valve. The port I42 is continuously connected to the port I34 whereby the channel I33 is always maintained under pressure by the feed pump.

Each of the reversing valves H9 and I28 have an exhaust port I43 and I44 respectively which are connected by channels I45 and I46 to ports I41 and I48 of a control valve I49. This valve has a plunger I50 which is normally urged in one direction by a spring I5I to an automatic tracer control position. It may be moved by a rotatable crank I52 against the resistance of spring I5I to a manual control position and latched in that position by a spring-pressed latching lever I53 which is engageable with a lug I54 projecting from the crank I52. When the plunger I50 is in the position shown the ports I41 and I48 are connected by grooves in the plunger to exhaust ports I55 and I56 respectively.

The reversing valve plungers H9 and I28 are held by springs I51 into engagement with an eccentric I58 which is operatively connected to a gear I59. The rotary position of the eccentric determines the relative positions of the reversing valves and thereby the direction of resultant movement of the cutter. The gear I59 is connected through an intermediate idler I60 to a pinion I6I integral with a rotatable hydraulic motor I62. The hydraulic motor is connected by channels I63 and I64 to ports I65 and I66 respectively of valve I49. When this valve is in the position shown, these ports are connected by annular grooves in the valve to reservoir ports I61 and I68.

It should now be evident that the two reversing valves H9 and I28 are hydraulically connected directly to the opposite ends of the table cylinder, and to the opposite ends of the vertical cylinder I9 respectively for controlling reversible operation of the connected slides. The particular manner in which these valves control or proportion the flow to these two cylinders to proportion the rates of simultaneous movement thereof is more particularly described and claimed in the co-pending U. S. application Serial No. 409,171, filed September 2, 1941, now Patent No. 2,332,533, issued October 26, 1943. It is sufficient to say that the eccentric I58 may be rotated manually by the hand wheel I69 shown in Figure 4 to control the direction of resultant movement of the table and vertical slide, or in other words, control the path of movement of the cutting tool I10 shown in Figure 2 which is attached to a rotatable spindle I1I mounted in the spindle carrier 21. This manual rotation may be accomplished with the valve I50 in the position shown because at that time the hydraulic motor I60 is connected to reservoir and thus ofiers no resistance to the movement. 9

The tracer valve I03 controls automatic rotation of eccentric I58 and has a valve plunger I12 which is normally urged in one direction by a spring I13 and when the tracer is out of engagement with the pattern the plunger I12 may be urged to its lowest position as viewed in Figure 11 which results in a port I14 being connected to a reservoir port I15. The port I14 has a channel I16 which branches to a first cylinder I11 containing a piston I18 operable to disengage the latch I53, and to a second cylinder I19 containing a piston I for disengaging the latch I09. The tracer valve has four pressure ports I80, I8I,

I82 and I83 which are all supplied through a branch I84 of the supply line I33.

When the tracer finger I04 engages a pattern or other object it causes through the ball and socket connection I85, shown in Figure 4, an axial movement of the plunger I12 to the right as viewed in Figure 4 or upward as viewed in Figure 11 whereby annular groove I86 interconnects pressure port I8I with port I14. This results in an immediate flow of fluid pressure to cylinders I11 and I19 whereby the latch levers I53 and I09 are withdrawn, causing plunger I50 to shift down, and the plungers 58 and M to shift to the left and to the right respectively by spring 0. This places the eccentric I58 under automatic control of the tracer I04.

The motor ports I65 and I66 now become connected to ports I81 and I88 and thereby through channels to tracer valve ports I14 and I89 respectively. Since the channel I16 is already under pressure as previously explained and has a branch connection to port I81, fluid pressure will flow through channel I63 to cause rotation of the hydraulic motor I62. This is permissible because the port I89 is connected to the exhaust port I15. The hydraulic motor will continue to rotate until the tracer finger is held in a balanced position by the pattern with the tracer valve I12 in a central position. This means that the pattern is acting to restrain excessive deflection of the tracer and that the spring I13 is continuously urging the tracer into engagement with the pattern.

A balanced condition will bereached in which the spool I90 of the tracer valve is centralized with respect to the port I15 and a second spool I9I is centralized with respect to a reservoir port I92. When the spool I90 is centralized with respect to the port I15 flow either to or from the motor I62 will be stopped whereby the motor will stop, and the parts are now conditioned whereby any shift in movement of the spool I90 will cause connection of the pressure port I8I to either the port I14 or port I82 to port I89.

This portion of the tracer valve now acts as a reversing valve to control reversible rotation of motor I62 and a resultant variation in the direction of movement of the table and vertical slide, the other spool I9I, being centralized with respect to the port I92, will act as a resistance to control the return flow from the slide reversing valves through channels I45 and I46 respectively.

Due to the downward shifting of the plunger I50, the ports I41 and I48 will become connected to ports I93 and I94 and thereby through channels I95 and I96 to ports I91 and I98 in the tracer valve. Attention is invited to the fact that when the tracer valve is centralized or in a neutral position the ports I91 and I98 are partially open and the spool I9I is smaller in width than the port I92 whereby a pressure opening exists on either side of the spool to permit return flow from both of channels I95 and I96 to the reservoir channel I99. It will now be evident that any shift of the tracer valve and thereby of the spool I9I in either direction will restrict the fiow from both of channels I95 and I96 to the reservoir line I99.

This restriction of flow in channels I95 and I96 tends to slow down the rate of operation of the table and vertical slide during a change in their direction of movement caused by rotation of the hydraulic motor I62. It should now be clear that the tracer finger I04 can be connected to automatically control the path of movement of the cutting tool in two directions, or in other words, in any direction in a vertical plane and that by shifting the valve plunger I50 and latching it in the position shown in Figure 11 that'the relative direction of movement of the cutting tool with respect to the work may be manually guided or controlled by the steering wheel I69 and that this control may be cut out or stopped by the shifting of valve plungers 58 and 4I into the position shown in Figure 11, resulting in the two cylinders I3 and I9 being reconnected to the servo-valves for control thereby.

The crank I 52 which operates the control valve I50 is mounted on a shaft 200 which projects through the top of the tracer valve housing 20I as shown in Figure 4 where it is provided with a control knob 202. The crank I01 which is operatively connected to the valve plungers 4I and 58 and mounted on the shaft I08 may be rotated by a crank 203 as shown in Figure 1 which is operatively connected by linkage 204 to a lever 205 shown in Figure2 which is secured to the upper end of a rotatable rod 206. This rod is provided with an operating handle 201 whereby upon rotation thereof the lever I01 may be rotated. It will be noted that the latch I09 can only be disengaged by hydraulic pressure in the cylinder I19 and therefore when the latch is engaged the lever I01 cannot be manually rotated. Therefore, the lever 201 can only be utilized to rotate the crank I01 in a clockwise direction, but not in a counterclockwise direction.

The in and out movement of the spindle carrier 21 toward and from the work support, or in other words, the depth control movement may be automatically controlled by the tracer I06 previously referred to, and this tracer which is shown in detail in Figure 3 has a ball and socket connection indicated generally by the reference numeral 208 with the valve sleeve 209. A spring 2I0 acting on the upper end of the sleeve and operating through the ball and socket connection tends to hold the tracer I06 in a central or undeflected position, the tracer being provided with a spherical journal 2I I- by which it is supported in the end of the housing I05.

-Upon lateral deflection of the tracer the valve 209 will be caused to move axially toward the right as viewed in Figure 3. When the tracer is undeflected a pressure port H2 in the valve housing and supplied from channel I 33 is connected by an annular groove 2I3 to channel 2I4 which terminates in a port 2I5 of valve 14. Another port 2I6 in the tracer is connected by annular groove 2 I 1 to a reservoir port 2I8.

The port 2I6 is connected by a channel 2I9 through a direct connection to a port 220 in valve 14, and a branch connection to a port 22I but this connection is through a. resistance coll 222.

The valve plunger 14 is normally maintained in the position shown by a spring-pressed plunger 223 and the bore in which this plunger slides is connected by adrilled hole 224 to port 2I5 whereby whatever fluid pressure exists in channel 2I4 is communicated to the end of the plunger 223 to assist in holding the plunger 14 in the position shown. When the tracer I06 is deflected the pressure port 2 I2 is connected by the annular groove 2I1 to port 2I6,whereby the fluid pressure will flow through the resistance 222 and port 22I to the chamber 225 at the lower end of plunger 14, thereby urging that plunger upward against the resistance of the spring-pressed plunger 223.

This movement will be suflicient to connect port 2| by way of annular groove 226 to chanway of annular groove nel 18, and port 220 by 221 to channel 11. The channels 11 and 18 leading from opposite ends of the cylinde 28 are thus automatically connected to the tracer controlled valve I05 upon deflection thereof. The valve 14 thus serves to automatically disconnect the cross slide cylinder 28 from the servo-control valve 05 and connect it to the tracer control valve when the tracer I06 is deflected by a pattern or master. Such deflection may be effected by rotating the servo-screw to feed the cross slide in, and as soon as the tracer engages the master and becomes deflected sufficiently to shift the tracer control valve to cause admission of pressure to port 22I, the change-over is automatically effected.

In addition, the valve 13 has a pressure port 229 which becomes connected to port 230 via groove 23I whereby fluid pressure is forced through a check valve 23I' into channel 232 and thereby to cylinder 233. This cylinder contains a piston 234 for disengaging the half nut 235 from the servo-screw. This is necessary because slide actuation is now effected directly by the piston 29 and since no rotating the servo-screw ease the nut.

Attention is called at this point to another interlock which exists between the servo-screw 80 and the other tracer controlled valve in that in rotating the servo-screw 80 to feed the cross slide in, the operator may cause accidentalengagement of the tracer finger I04 with a master or other part of. the work support while setting up the machine and cause damage or breakage of the parts. To prevent this the tracer valve I 03 is provided with the pressure port I80 as'previously mentioned and when the plunger I12 is excessively shifted in an axial direction the port I80 is connected by an annular groove 236 in plunger I12 to a port 231 which is also connected to channel 232 leading to cylinder 233 in the cross slide housing which contains the piston 234. This piston is adapted to engage the end of a pivoted nut member 235 and cause disengagement of the nut member from the servo-screw 80, thereby rendering the screw inefiective to cause further movement of the cross slide, or in other words s opping the Cross slide so as to prevent damage to the tracer finger.

' There has thus been provided a hydraulic control circuit for controlling three-directional rel ative movement automatically and simultaneously between a cutting tool and a work support which utilizes two tracers, one of which controls reversible operation in two of said directions, and the otherof which controls reversible operation in a third direction and including means wherebyeither of said tracers may be rendered ineffective simultaneously rendering manual controls eifective; means whereby only one of said tracers may be rendered ineii'ective so that manual steering in a givenplane is rendered possible; and suitable interlocks between the tracer control it is necessary to disendirections either by manual or power-means.

The structure for supporting these tracers for independent operation in guiding the relative movement between the tool and work and in a manner each independent of the other will now be explained. It will be noted from Figures 1 and 2 that the spindle carrier 21 is supported for two-directional movement, and this spindle carrier has a self-contained transmission including a prime mover 238 which is attached to the rear of the carrier by a bracket 239 so as to be movmeans are provided for able therewith for driving the spindle I'll which holds a cutting tool I18. Opposite the cutting tool and mounted on the table II is a work supporting bracket 240 and on top of that is a pattern or master supporting bracket MI. The bracket 24I rests on the top surface of the bracket 248, and a central pivot 242, Figure 9, interconnects the same whereby the bracket may be angularly adjusted. In addition, the upper bracket may be adjusted back and forth by the adjusting screw 242'.

Thus, the face 243 may be adjusted relative to the face 244 of the bracket 248. The screws 243' at either end serve to swivel the upper bracket. The purpose of this adjustment is that after the pattern or master is attached or bolted into place on the face 243 the longitudinal surfaces may be slightly out of line with the direction of travel of the table and by this simple adjusting means correction may be easily effected without disturbing the various clamping means by which the pattern or master has been secured in place.

In a tracer controlled machine of the character described it is necessary that the tracer partake of the movement imparted to the cutter in order that control may be maintained. Since the two tracers I84 and I86 are coupled for control of a single tool it is necessary that they be responsive to the movements of the spindle carrier and therefore are mounted on the carrier.

To this end a tracer bracket, indicated generally by the reference numeral 245 in Figures 1 and 2, has been provided with a dovetail guide 246 formed on the bottom thereof for reciprocation in the dovetailed guideway 241 formed on the top of the spindle carrier 21.

Referring to Figure 5 the underside of the dovetail guide 246 is provided with rack teeth 248 which are adapted to be engaged by a pinion 249 which is attached to the end of a shaft 258 which is journaled in the carrier 21 and provided with a hand wheel 25I shown in Figure 2. Rotation of this hand wheel serves to adjust the tracer bracket toward and from the pattern support and also relative to the cutting tool I18.

The tracer bracket is provided with a vertical guideway 252 on one face upon which is mounted a saddle 253 for carrying one of said tracers and a saddle 254 for carrying the other tracer.

Means are provided whereby these saddles may be independently adjusted relative to one another and this means comprises two elevating screws 255 and 256. These screws are journaled for rotation in opposite ends of the bracket and as shown in Figure 5 the lower end of screw 256 is provided with a bevel gear 251 and the lower end of screw 255 is provided with a bevel gear 258. The screw 256 is threaded in a nut 259 carried by the saddle 253.

The screw 256 is adapted to be manually rotated to eifect adjustment of the saddle 253 by means comprising a bevel gear 268 which is' keyed to a shaft 26I in a position to mesh with the bevel gear 251. The shaft 26I extends longitudinally through the base housing 262, Figure 2, of the bracket 245 where it is provided with another bevel gear 263 for engagement with a bevel gear 264 attached to the end of a shaft 265 which is journaled in the wall of the housing 262 and provided with an operating handle 266. It will now be evident that rotation of the handle 266 will effect adjustment of the saddle 253 which supports the two-directional tracer I84.

The bevel gear 258 which operates the screw 255 is similarly connected through bevel gearing 10 and connecting shaft indicated generally by the reference numeral 261 in Figure 5 to an operating handle 268 mounted on the rear of the housing 262 as shown in Figure 2 and adjacent to the lever 266.

The saddle 253 carries a knee 269 which is supported in guides 218 and 2H formed on the saddle and translation or adjustment is effected by means of a rack bar 218 which is attached to the saddle, and a pinion 21I which intermeshes with the rack and is attached to the end of a shaft 212 which is journaled in the knee and provided with an operating handle 213. The knee 269 is provided with guide surfaces 214 and 215, Figure 4, for guiding the tracer housing 28I The tracer housing 28I contains the tracer control valve I83, the selector control valve I49, the two reversing valves I28 and H9, together with the eccentric I58 and the power driving mechanism therefor including the hydraulic motor I 62.

The eccentricity of the eccentric means I58 may be varied or adjusted by the truncated cylindrical member 216 which has a shifter collar 211. As shown in Figure 5 this collar is engaged by an eccentric pin 218 attached to the end of a shaft 219 journaled in the wall of the housing and this shaft is provided with a gear segment 288. A pinion 28I attached to the end of a shaft 282 serves to rotate the segment and thereby the pin 218 to shift the collar 211.

The shaft 282 is journaled in a plate 283 and provided with a bevel gear 284 which intermeshes with a bevel gear 285 arranged at right angles thereto. The bevel gear 285 is attached tothe end of a shaft 286 which is journaled in a housing 281. The housing 281 is bolted to the plate 283 and this plate is capable of limited angular adjustment to change the angle of the depending shaft 286 to suit the convenience of the operator.

This is accomplished by providing the plate 283 with elongated slots 288 at opposite ends as shown in Figure 10 through which pass clamping bolts 289. The shaft 286 extends through pendant arm 298 which is secured to the housing 281 and the projecting end of the shaft 286 provided with an operating lever 29I. A graduated collar 29Ia is fixed with handle 29I and movable therewith relative to a fixed reference mark 29Ib to indicate the feed rate setting. This makes a convenient arrangement whereby the operator may change the rate of tracing or relative feeding between cutter and work from his position on the floor.

The tracer housing 28I may be adjusted on the guideways 214 and 215 by means of a screw 292 which is threaded in a nut 293 depending from the underside of the housing 28I. The screw is journaled in opposite ends of the knee and is provided with a square and 294 as shown in Figure 5 for attachment of a. removable wrench.

The saddle 254 is supported on the guideways 252 and operatively connected to the screw 255 by a half nut 295 as more particularly shown in Figure '7. The half nut is formed on the end of a retractable plug 296 which is slidably mounted in the saddle 254 as more particularly shown in Figure 8. The plug is held against rotation by a pin 291 engaging a slot 298 formed longitudinally of the plug. A pin 299 eccentrically mounted on the end of a shaft 388 engages a slot 38I formed in the plug whereby rotation of the shaft will effect disengagement of the half nut 295. The shaft 388 may be rotated by a handle 382 locked to effect shifting of the nut.

To insure against any possibility of the saddle dropping when the nut is disengaged a counterbalance is provided comprising a counterweight l 334 shown in Figure which is connected by a tracer bracket so that a plate template lying in a horizontal plane may be utilized as a pattern for the depth control tracer which would be possible where the work is to have a uniform cross section. This would be produced by reciprocating the table, and at the end of each table stroke indexing the cutter laterally, i. e., in a vertical direction.

By looking the saddle against vertical movement this indexing movement would not be imparted to the tracer whereby it would remain in alignment with the plane of the template. To this end the saddle 254 is provided with a detachable bracket 303, more particularly shown in Figures 3 and 6, which may be secured to the saddle 254 by a pair of screw threaded members 304 having knurled operating knobs 305. The bracket is provided with a key 303 which is adapted to fit in a key slot 301 formed'on the saddle 254. The upper end of the bracket is provided with a roller 303 which is adapted to fit in a longitudinally extending slot 309 formed on a fixed support 3I0. This fixed support is secured as by bolts 3 I 2 to the end of a gooseneck arm 3 I3 which, as shown in Figure 1, is attached to the top of the column I5. By providing the roller connection it will be obvious that the tracer support will move toward and from the work support whenever the carrier 21 is moved, but when the carrier is moved vertically by the slide I1 the tracer bracket 245 will move up and down relative to the saddle 254.

An interlock is provided to insure that the half-nut 295 is disengaged from the screw 255 whenever the bracket 303 is placed in position and this includes an interlock pin 3 which is slidably supported in a bore 3I5 in the saddle 254 and adapted to project into key slot 301 s shown in Figure 7 whereby when the bracket is placed in position the key 306 will shift the interlock pin to the right as viewed in Figure 7. The interlock pin has a bevel connection 3I6 with the end of a shifter rod 3I1 which is continuously urged in one direction by a. spring 3I8. The rod 3" has a slot 3I3 into which fits a pin 320 mounted crosswise of the shaft 300 as shown in Figure 8. Therefore, when the shifter rod 3" is depressed it will cause rotation of the shaft 300 and thereby through the eccentric connection 299 cause withdrawal of the half-nut 235.

With the upper carrier clamped against vertical movement and the tracer bracket 245 free to move up and down there is a possibility of collision be- 12 which has a second shoulder 323 engaging the end of a pivot lever 321. The other end of the lever engages a trip rod 323 which is normally urged in one direction by a spring 329 interposed between a fixed part of the support 3 I0 and a collar 330 attached to the rod.

When the rod 322 is pushed upward it rotates the rocker shaft and thereby the lever 321 and pushes the trip rod 328 upward against the resistance of spring 329 and causes actuation of the limit switch 32 I.

tween these two brackets and in order to prevent damage to the parts an interlock is provided which is effective to reduce the pump pressure in the system because such a movement would be produced by the introduction of fluid pressure to the lower end of cylinder I9 as viewed in Figure 1. This is accomplished by providing a limit switch 32I which when operated shuts down the motor 32I that drives the pumps I38 and I31.

The saddle 254 as shown in Figure 6 has a rod 322 slidably mounted therein and projecting below the lower end thereof for engagement by a lug 323 formed integral with the saddle 253 as shown in Figure 5. The upper end of the rod 322 engages a shoulder 324 on a rocker shaft 325 Occasion may arise where it may be desirable to utilize a plate template with the lower tracer I04, in which case the tracer could not be responsive to in and out movements of the carrier 21 as dictated by the upper tracer I00. Means have, therefore, been provided for rendering the lower tracer support non-responsive to control movements of the upper tracer. This means comprises an arm 33I which is attached to the top of the vertical slide I1 as indicated in Figure 1. As shown in Figure 4, this arm has a slotted plate 332 attached to the end thereof and the cross slide 269 of the lower tracer support has a gooseneck arm 333 projecting from the rear end thereof in which is mounted a bar 334 which is of rectangular cross-section and is positioned to extend across the face of the plate 332. The bar 334 supports a clamping member indicated generally by the reference numeral 335 and this clamping member comprises front and rear members which are hinged together by a pin 336.

The clamping bolt 331 is pivotally connected to the rear member by a pin 333 and is adapted to swing down between a pair of ears 339 formed on the front member. A threaded member 340 is threaded on the bolt and is adapted to draw the front and rear members together in clamping engagement with the bar 334. The clamping member carries a roller 34I which fits in a slot 342 in the plate 332. It will, therefore, be apparent that when the bar 334 is clamped to the plate 332 by the clamping member that the slide 269 is held against axial movement but the entire structure is still capable of vertical movement. When thisl is done, handle 213 is pulled out to disengage the pinion from the rack.

Iteis thus possible to hold the tracer axial I06.

Remote control means have been provided for actuating the depth control tracer valve in such a manner as to effect disengagement of the tracer from its pattern. Referring to Figure 11 it was stated supra that the valve 13 is automatically shifted upon deflection of the tracer I08 to effect control connection between the tracer valve and the cylinder 20. Once this connection is established it can only be broken by shifting the tracer control valve in a direction corresponding to excessive deflection of the tracer, or, in other words, interconnection of ports 2| 2 and 2I6.

Since the tracer I06 is inaccessible to an operator standing on the floor beside the machine a remote control connection is provided for this purpose.

This includes a remote control flexible shaft indicated generally by the reference numeral 342 in Figure 3. The flexible wire 343 which extends through a flexible sleeve 344 is connected, to an operating rod 345 which has heads 346 and 341 formed on opposite ends thereof. The rod 345 is slidable relative to a cover plate 348 attached to the end of the tracer valve plunger 209. A spring 340 acts on the head 34'! to hold the rod I04 against movement as dictated by the upper tracer 13 in such a position that the head 343 will not interfere with the normal operation of the valve.

When it is desired to shift the valve the wire 343 is pulled until the head 346 engages the plate 348 against the resistance of spring 349 after which further movement will shift the valve plunger to efiect the necessary interconnection of ports H2 and 2l6 which will cause admission of fluid pressure to cylinder 28 in such a direction as to move the tracer out of engagement with the pattern and after the separation has been effected the wire 343 is released whereupon the tracer valve assumes its normal undeflected position under the influence of spring 2H1.

This will result in the port 2l6 becoming connected to the exhaust port 2l8, thereby relieving the pressure on the lower end of piston 14 which will be returned to its normal position and thereby disconnect the tracer from control of the piston 29.

The flexible sleeve 344 is connected to a fixed bracket 350 and the wire is connected at 35l to a collar 352 attached to a rod 353. This rod is slidable within the tubular member 206 which as shown in Figure 12 has a pair of elongated slots 354 formed in opposite sides thereof. A pin 355 which passes through the rod 353 extends through these slots to connect the hand grip 356 to the rod.

It will now be obvious that by vertical movement of the hand grip 353 the tracer valve may be remotely controlled to effect disengagement of the tracer by pulling upward on the hand grip. The tracer valve housing I05 is slidably connected by a dovetailed guideway 351 on a knee 358 and cross movement thereon is effected by the cross screw 359. A clamping member 350 is threaded in the tracer valve housing support for clamping the parts after adjustment. The knee 358 is supported by dovetailed guideways 36l for movement relative to the bracket 254 by means of an adjusting screw 362 having an operating handle 363.

By means of the two adjusting screws 359 and 363 relative adjustment may be efiected between the tracer I06 and tracer I04.

There has thus been provided an improved automatic profiling and die-sinking machine which utilizes a pair of tracers, one of which automatically controls universal movement in a plane and r the other of which automatically controls relative movement between a tool and a work piece in a direction at right angles to said plane.

What is claimed is:

1. In a pattern controlled machine tool having a cutter support and a work support mounted for three-directional relative movement, the combination of means for automatically controlling the three directions of movement simultaneously including a first pattern controlled automatic tracer for governing two directions of said movement, a second pattern controlled automatic tracer for governing a third direction of said relative movement, said tracers being mounted on one of said supports, said other support being adapted to support patterns in opposition to said tracers, and control interconnections rendering each tracer adaptable to control at least one direction of relative movement between the other tracer and its pattern.

2. In a pattern controlled machine tool having a cutter support and a work support mounted for three-directional relative movement, the combination of means for automatically controlling the three directions of movement simultaneously including a first pattern controlled automatic tracer for governing two directions of said movement, at second pattern controlled automatic tracer for governing a third direction of said relative movement, said tracers being mounted on one of said supports, said other support being adapted to support patterns in opposition to said tracers, control interconnections rendering each tracer adaptable to control at least one direction of relative movement between the other tracer and its pattern, and means for rendering one of said tracers non-responsive to a direction of movement controlled by the other tracer.

3. In a pattern controlled machine tool having a cutter support and a work support mounted for three-directional relative movement, the combination of means for automatically controlling the three directions of movement simultaneously including a first pattern controlled automatic tracer for governing two directions of said movement, a second pattern controlled automatic tracer for governing a third direction of said relative movement, said tracers being mounted on one of said supports and the other support being adapted to support patterns in opposition to said tracers, control interconnections rendering each tracer adaptable to control at least one direction of relative movement between the other tracer and its pattern, and means for rendering either tracer non-responsive to the control action of the other tracer.

4. In a pattern controlled machine tool having a cutter support and a work support mounted for three-directional relative movement, the combination of means for automatically controlling the three directions of movement simultaneously including a first pattern controlled automatic tracer for governing two directions of said movement, a second pattern controlled automatic tracer for governing a third direction of said relative movement, said tracers being mounted on one of said supports, said other support being adapted to support patterns in opposition to said tracers, control interconnections rendering each tracer adaptable to control at least one direction of relative movement between the other tracer and its pattern, and selective means for rendering either tracer non-responsive to a controlled direction of movement of the other tracer.

5. In a pattern controlled machine tool having a work support and a tool support, means mounting the tool support for two directions of relative movement, a pair of tracers mounted on the tool support for cooperation with patterns carried by the work support, control connections from one of said tracers for controlling one direction of movement of the tool support, control connections from the other tracer for controlling the other direction of movement of the tool support, means to render one of said tracers nonresponsive to the movement controlled by the other tracer, and interlock means to prevent collision of said tracers when one of them is held against movement.

6. In automatic control means for a pattern controlled machine tool, the combination of a pair of tracers, individual supports for each tracer, a common support for said tracer supports, means to effect adjustment of one of said tracer supports independently of the other including a rack and pinion, means to disconnect the pinion from said rack, a fixed support for said'common support, means to connect the adjustable tracer support to the fixed support whereby upon movement a bed, a work support umn, a spindle carrier mounted on the column matic tracer of said common support only one tracer support will be moved.

7. In a pattern controlled machine tool haying mounted thereon, a colfor vertical and horizontal movement, a tracer support mounted on the top of the carrier for movement therewith, means on the carrierfor adjusting the tracer support toward the work support to effect control engagement of the tracer with a pattern, a vertical rod supported by the column, a remote control flexible shaft coupling the rod with the tracer whereby actuation of the rod will cause movement of the tracer valve in a direction to eifect disengagement of the tracer from the pattern.

8. In a pattern controlled machine having a bed, a work support slidably mounted on the bed, a column, a spindle'carrier mounted on the column for two-directional movement, a pair of tracers mounted on the carrier, a control valve associated with each tracer, a selector valve mounted on the column for connecting and disconnecting one of said tracer control valves with operating means for the movable parts, telescoping control elements mounted on the column, means connecting one of said elements to the selector valve, means to rotate said element to effect shifting of said selector valve, means connecting the other element to one of said tracer valves, and means to effect axial movement of the element to shift the tracer valve.

9. In a pattern controlled machine tool. having a work support and a tool spindle carrier supported for relative movement in a plurality of directions and a pair of tracer supports carrying automatic tracers mounted on said carrier, the combination of means for adjusting said tracer supports relative to one another including individual translating screws, means to disconnect one tracer support from its translating screw, a counterbalance for the disconnected tracer support and meansto connect said dis- "connected tracer support to a fixed part of the machine whereby said spindle carrier may move without moving said disconnected tracer support.

10. In a pattern controlled machine tool having a cutter support and a work support, and means mounting said supports upon the machine tool for relative movement in three directions, the combination of means for automatically effecting and controlling said movement including a rotatable direction determinator, a first pattern controlled automatic tracer operatively connected for actuating said direction determinator and thereby determining the resultant of two of the directions of relative movement, and asecond pattern controlled autofor governing a third direction of relative movement between said supports.

11. In a pattern controlled machine tool having a cutter support and a work support, and means mounting said supports for three-directional relative movement, the combination of a pair of tracer mechanisms mounted on one support for engaging separate patterns carried by the other of said supports, servo-motor mechanisms each including a manually operable control for producing each of said three directions of movement, one of said mechanisms being operable to move the tracers toward their respective patterns, means to render said mechanism inoperative upon engagement of the first tracer with (pair of tracer. supports its respective pattern, and other means for adlusting the other tracer in engagement with its pattern. L

12. In a pattern controlled machine tool having a cutter support and a work support, the combination with means for mounting said supports for three-directional relative movement of individual manually operable servo-motor mechanisms for each of said directions of relative movement, a tracer mechanism having a defiectable tracer mounted on one of said supports for automatic control by a pattern carried by the other support, disconnect devices associated with each servo-motor mechanism for rendering the same non-responsive to manual actuation, and means operable by the tracer upon initial deflection thereof during movement in any direction by any of said servo-motor mechanisms to effect simultaneous disengagement of all of said disconnecting devices.

13. In a pattern controlled machine tool having a work support and a tool spindle carrier mounted on the machine for relative. movement in a plurality of directions and a tool spindle journaled in said carrier, the combination of a mounted onthe machine and each, having a tracer extending substantially parallel to the axis of said spindle, means for adjusting said tracer supports relative to one another including individual translating screws, means to disconnect one tracer support from its translating screw and connect it to a fixed part of the machine whereby the-spindle carrier may be bodily moved with respect to said tracer to change the spacing between said cutter spindle and tracer.

14. In a pattern controlled machine tool having a work-support and a tool spindle carrier mounted-on the machine for relative movement in a plurality of directions, a tool spindle journaled in said carrier, said carrier having a guideway formed therein parallel to the axis of the spindle, the combination of a bracket mounted on said guideway, means to adjust said bracket parallel to the axis of the spindle, a pair of slides mounted on said bracket for sliding movement normal to the axis of said spindle, a tracer head mounted on each slide, a tracer mounted on each tracer head and extending substantially parallel to the axis of said spindle, and individual means to adjust each tracer head parallel to or laterally of said spindle axis to determine the spacing be tween the spindle and each of said tracers.

15. In a pattern controlled machine tool having a cutter support and a work support, said supports being mounted on the machine for three-directional relative movement, the combination of means for effecting and controlling said movement including a pair of automatic tracer control mechanisms, a tool spindle Journaled in the cutter support, tracer fingers associated with each of said tracer mechanisms and arranged in parallel relation to said cutter spi'ndle, means controlled by one of said mechanisms for determining the direction of lateral movement of said spindle, means controlled by the other tracer mechanism for determining axial movement of said cutter spindle, and rate control means associated with the first tracer control mechanism for determining the rate of scanning of the second tracer finger.

EDWARD W. YATES. IAFI s. ARMANDROFF'. 

